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1、機(jī)械設(shè)計(jì)課程設(shè)計(jì)計(jì)算說(shuō)明書(shū)設(shè)計(jì)題目 二級(jí)展開(kāi)式圓柱齒輪減速器專(zhuān)業(yè)班設(shè)計(jì)者指導(dǎo)教師2012年月類(lèi)_日交通大學(xué)城市學(xué)院c.U n2- I / 0.00 I 11II2 cosp cos13.1165.確定齒寬b = b = a(|) = 115 x 0.482 = 55.43mm2 a(5).驗(yàn)算輪齒彎曲強(qiáng)度1. 當(dāng)量齒數(shù)Z27cr ez =1 = 27.0(V1 C0S3 p C0S3 13.1160z =知=94 1?V2 C0S3 p COS313.116 2 .齒形系數(shù)和修正系數(shù)線性差法可得Y =2.586 Y =1.597FalSalY =2.174 Y =1.796Fa2Sa23. 重

2、合度系數(shù)Y重新計(jì)算端面重合度1.670bd IT Fa1 Sa155x55.446x2=60.852MPa o J=1.88 - 3.2_L +_ V cos13.116L 127 85 J J=1.6700 750 75Y = 0.25 + = 0.25 +- = 0.849螺旋角系數(shù)由。及,取 Y =0.835 .校核彎曲強(qiáng)度_ 2000KT y Y Y Ym 二2mmnZ|=27z2=85bo=55mmb =60mmd|二55.446 mm d7 = 178.661 mm a=115 mm3=13.116。= 2000KTy 丫 YYF2 bd IT! Fa2 Sa2 Pn=2000x1

3、.2x53.369 * 2.19x1 .78x 0.849x 0.8355x 55.446x 2 =57.88MPa Q F2(6) .設(shè)計(jì)結(jié)果齒輪參數(shù)及幾何尺寸模數(shù)m =2mmn齒數(shù) z=27 z =851乙齒寬 b2 =55mm b( =60mm分度圓直徑d =55.446 mmd2 = 178.661 mm中心距 a=115 mm螺旋角阡13.116齒輪精度8級(jí)齒輪材料小齒輪45鋼，調(diào)質(zhì)，230-250HBS大齒輪45鋼，正火，190-210HBS1. 低速級(jí)齒輪傳動(dòng)設(shè)計(jì)1) .齒輪材料，熱處理考慮此減速器小批量生產(chǎn)，為便于加工，故大小齒輪都選用軟齒面 漸開(kāi)線斜齒輪高速級(jí)小齒輪選用45鋼

4、調(diào)質(zhì)，齒面硬度230-250HBS ,取小齒輪齒數(shù)Z亡39高速級(jí)大齒輪選用45鋼正火，齒面硬度190-210HBS 5大齒輪齒數(shù) z = ix z = 2.3834 x39 = 92.953 取=101.212i = u = = II = 2359 誤差小于 5%12) .初步設(shè)計(jì)齒輪傳動(dòng)的主要尺寸.確定許用彎曲應(yīng)力 .彎曲疲勞極限應(yīng)力大齒輪S. =220MPaFlim小齒輪孔.二250MParlim.壽命次數(shù)應(yīng)力循環(huán)次數(shù)N = 60j n t = 60 x 1 x 309.387 x (8 x 250 x 8) = 2.970 x 10sF2 F 2N = 60j n t = 60 x 1

5、x 129.998 x (8 x 250 x8) = 3.120 x 10Y =0.93 Y =0.99 N2N2.試驗(yàn)齒輪應(yīng)力修正系數(shù)Y =2ST .最小平安系數(shù)按一般可靠度S . =1.25Fmin.許用彎曲應(yīng)力(1) .確定許用接觸應(yīng)力接觸疲勞應(yīng)力大齒輪。=550MPaHlim小齒輪。=580MPaHlim .壽命系數(shù)應(yīng)力循環(huán)次數(shù)N = 60j n t = 60 x 1 x 309.387 x (8x 250 x 8) = 2.970 x 13H2H 2N =60j n t = 60 x 1 x 129.9987 x (8 x 250 x 8) = 3.120 x 10?H3H 3Z =

6、0.92 Z =0.98 .最小平安系數(shù)按一般可靠度S . =1I Imin .許用接觸應(yīng)力% 171I = I = 0.616R 1.724螺旋角系數(shù)Z = Jcosp = vcos12 = 0.9890設(shè)計(jì)中心距(500KT f Z Z Z Z V1 a vH 7a (u1)a!500x1.2x158.609 (189.8x 2.46x0.616 x0.989 ! 0.591 x 2.3834=90.597mm= (2.3834 + 1)533.6、2a cosp 2x90.597 x cos 12 m =n z +z39 + 9212=1.353取m -2 ,重求中心距nm (z + z

7、 ) 2 x (39 + 92)a = cosp2 = 2xcos12 =135-927mm圓整中心距取a=135mm調(diào)整0P = arccos叫(匕 * % L 2a J2x(39 + 92) 一=arccos ,L 2x135 J=13.982(3) .確定齒輪參數(shù)尺寸取齒數(shù)Z二39z2=921. 模數(shù) m =2mmnz g23.實(shí)際齒數(shù)比u = 2- = = 2-359 z 3914.確定分度圓直徑=80.382mmm z, 2x39cosP cos 13.982生M _2x92_ = 189618mmcosp cos 113.982確定齒寬b = b = a(|) = 135x 0.5

8、91 = 78.785mm1 a取 b=b?=80mm2b1=b7+5=85mm.驗(yàn)算輪齒彎曲強(qiáng)度1.當(dāng)量齒數(shù)7QQ7 = =-= 42 AR3vi coss p COS3 13.98292COS313.982=100.987ZZ =2v2 COS3 P2. 齒形系數(shù)和修正系數(shù) 線性差法可得=2.37 Y =1.675FalSal=2.18 Y =1.79Fa2Sa23 .重合度系數(shù)Ys重新計(jì)算端面重合度( = 1.88-3.2 + cospa Lzz 力=1.88 3./ + cos 13.982L 139 92 J J= 1.7110.750.75Y =0.25 4-= 0.25 4=0.

9、68881.711a4 .螺旋角系數(shù)由。及8 1 ,取 Y =0.845.校核彎曲強(qiáng)度a = 2。 Y Y YYF1bd mFa1 Sa1 P1 n八八”八=x 2.37 x1.675x 0.688x 0.84 =80x80.382x2= 67.9MPaLy JF1o = 2。 y Y YYF2bd HlFa2 Sa2 P1 n=2000x1.2x158.609 * 2.18x1.776x0.688x0.84 80x80.382x 2=64.727MPa 31.37mmBF = F tan p = 3949.034 x tan 13.982。= 983.287Na2222、繪制軸的力學(xué)模型圖2

10、ao3求垂直面支反力，見(jiàn)圖2b。作垂直面彎矩圖2c由繞支點(diǎn)A的力矩和Zm=0 得：-LF -(I +l )F -(I +l +l )F =01 t1 12 t2 123 DVFdv =-3184N方向向上同理，由由繞支點(diǎn)D的力矩和ZLm= 0得.DV 嚀-(I +l +l )F +(l +l )F +L F =0123 AV 23 t1 3 t2Fav =2540.991N 方向向上M = /M f2Du +M 2 DX/ = 20390.3952 +1576082 = 158921N mmBBHBVD處:M = JM2cu + M2=也6138.5612+155000 2 = 157188N

11、，mmCCHCV6.轉(zhuǎn)矩圖，見(jiàn)圖2goT =T = 158609N - mm2 n7當(dāng)量彎矩比擬M、M、可知，當(dāng)量彎矩最大處是C截面處B CZM =Be SxDA則 A =S = 1280NDDA =F + S = 1932.909NAxDA需有所得的A值驗(yàn)證一下，比值一 =0.058與試取界限值cC。or時(shí)的相應(yīng)比值是否相等：A 1 28Ad = 0.0396與對(duì)應(yīng)的誤差較大C 32.3CororA1 932A= 一 =0.0598與試取的 已很接近C 32.3CororD、參照上次試算結(jié)果，重新取界限值e軸和 重新取e = 0.4125S =eR = 0.4125x3213 = 1325N

12、DDS =eR = 0.4125 x 2562.934 = 1065.8NAA則 A = 1325NDA 1.325A再驗(yàn)證_d_ =0.00410 ,與對(duì)應(yīng)的 =0.0411已很C 32.3Coror接近3、計(jì)算軸承的當(dāng)量動(dòng)載荷P、 P12軸承AA 1932.909a- = 0.75 eR 2562.934aA* =0.44Y=1.30A1P =f (X R +Y A )= 4368.56AP A AA A軸承DA 1325 苛- 3213 = aD查表 17-5* =1 Y =0D1P =f R = 1.2x3213 = 3855.6Dp D4、由預(yù)期壽命求所需的CPP ,即應(yīng)按軸承2計(jì)算AD=41916C = 16000F A 106十一.t鍵的選擇與校核低速軸上鍵：低速軸伸出段軸端處軸徑d=48mm 軸轂長(zhǎng)110mm查表得b=14mm h=9mm L= 100mm采用A型普通平鍵 45鋼 查表得o = 100200MPa鍵的工作長(zhǎng)度l=L-b=86mma=37.533MPaC = 16000 b二 14mmh=9mmL= 100mm由于減速器屬于中小型，查表